Maintenance Fundamentals Episode 2 part 3 pptx

Figure 12.4 Bull gear centrifugal compressor.Because of their cantilever design and pinion rotating speeds, bull gear compres-sors are extremely sensitive to variations in demand or down

Balancing Piston

To Discharge Balancing Lineto Suction

Shaft Seal

Figure 12.3 Balancing piston resists axial thrust from the inline impeller design of a centerline centrifugal compressor

impellers tend to cancel the axial forces generated by the preceding stage This design is more stable and should not generate measurable axial thrusting This allows these units to contain a normal float and fixed rolling-element bearing Bull Gear

The bull gear design uses a direct-driven helical gear to transmit power from the primary driver to a series of pinion-gear-driven impellers that are located around the circumference of the bull gear Figure 12.4 illustrates a typical bull gear compressor layout

The pinion shafts are typically a cantilever-type design that has an enclosed impeller on one end and a tilting-pad bearing on the other The pinion gear is between these two components The number of impeller-pinions (i.e., stages) varies with the application and the original equipment vendor However, all bull gear compressors contain multiple pinions that operate in series

Atmospheric air or gas enters the first-stage pinion, where the pressure is in-creased by the centrifugal force created by the first-stage impeller The partially compressed air leaves the first stage, passes through an intercooler, and enters the second-stage impeller This process is repeated until the fully compressed air leaves through the final pinion-impeller, or stage

Most bull gear compressors are designed to operate with a gear speed of 3,600 rpm In a typical four-stage compressor, the pinions operate at progressively higher speeds A typical range is between 12,000 rpm (first stage) and 70,000 rpm (fourth stage)

Figure 12.4 Bull gear centrifugal compressor.

Because of their cantilever design and pinion rotating speeds, bull gear compres-sors are extremely sensitive to variations in demand or down-stream pressure changes Because of this sensitivity, their use should be limited to base load applications

Bull gear compressors are not designed for, nor will they tolerate, load-following applications They should not be installed in the same discharge manifold with positive-displacement compressors, especially reciprocating compressors The standing-wave pulses created by many positive-displacement compressors create enough variation in the discharge manifold to cause potentially serious instability

In addition, the large helical gear used for the bull gear creates an axial oscilla-tion or thrusting that contributes to instability within the compressor This axial movement is transmitted throughout the machine-train

PERFORMANCE

The physical laws of thermodynamics, which define their efficiency and system dynamics, govern compressed-air systems and compressors This section dis-cusses both the first and second laws of thermodynamics, which apply to all compressors and compressed-air systems Also applying to these systems are the Ideal Gas Law and the concepts of pressure and compression

First Law of Thermodynamics

This law states that energy cannot be created or destroyed during a process, such

as compression and delivery of air or gas, although it may change from one form

of energy to another In other words, whenever a quantity of one kind of energy disappears, an exactly equivalent total of other kinds of energy must be pro-duced This is expressed for a steady-flow open system such as a compressor by the following relationship:

Net energy added

to system as heat

and work

þ

Stored energy of mass entering system

Stored energy of mass

Second Law of Thermodynamics

The second law of thermodynamics states that energy exists at various levels and

is available for use only if it can move from a higher to a lower level For example, it is impossible for any device to operate in a cycle and produce work while exchanging heat only with bodies at a single fixed temperature In thermo-dynamics, a measure of the unavailability of energy has been devised and is known as entropy As a measure of unavailability, entropy increases as a system loses heat but remains constant when there is no gain or loss of heat as in an adiabatic process It is defined by the following differential equation:

dS¼dQ T where

T¼ Temperature (Fahrenheit)

Q¼ Heat added (BTU)

Pressure//Volume//Temperature (PVT) Relationship

Pressure, temperature, and volume are properties of gases that are completely interrelated Boyle’s Law and Charles’s Law may be combined into one equation that is referred to as the Ideal Gas Law This equation is always true for Ideal gases and is true for real gases under certain conditions

P1V1

T1

¼P2V2

T2 For air at room temperature, the error in this equation is less than 1% for pressures as high as 400 psia For air at one atmosphere of pressure, the error

is less than 1% for temperatures as low as
2008 Fahrenheit These error factors will vary for different gases

Pressure//Compression

In a compressor, pressure is generated by pumping quantities of gas into a tank or other pressure vessel Progressively increasing the amount of gas in the confined

or fixed-volume space increases the pressure The effects of pressure exerted by a confined gas result from the force acting on the container walls This force is caused

by the rapid and repeated bombardment from the enormous number of molecules that are present in a given quantity of gas

Compression occurs when the space is decreased between the molecules Less volume means that each particle has a shorter distance to travel, thus propor-tionately more collisions occur in a given span of time, resulting in a higher pressure Air compressors are designed to generate particular pressures to meet specific application requirements

Other Performance Indicators

The same performance indicators as centrifugal pumps or fans govern centrifu-gal compressors

Installation

Dynamic compressors seldom pose serious foundation problems Since moments and shaking forces are not generated during compressor operation, there are no variable loads to be supported by the foundation A foundation or mounting of sufficient area and mass to maintain compressor level and alignment and to ensure safe soil loading is all that is required The units may be supported on structural steel if necessary The principles defined for centrifugal pumps also apply to centrifugal compressors

It is necessary to install pressure-relief valves on most dynamic compressors to protect them because of restrictions placed on casing pressure and power input and to keep it out of its surge range Always install a valve capable of bypassing the full-load capacity of the compressor between its discharge port and the first isolation valve

Operating Methods

The acceptable operating envelope for centrifugal compressors is very limited Therefore, care should be taken to minimize any variation in suction supply, backpressure caused by changes in demand, and frequency of unloading The

operating guidelines provided in the compressor vendor’s O&M manual should

be followed to prevent abnormal operating behavior or premature wear or failure of the system

Centrifugal compressors are designed to be base loaded and may exhibit abnormal behavior or chronic reliability problems when used in a load-following mode of operation This is especially true of bull gear and cantilever compressors For example, a 1-psig change in discharge pressure may be enough to cause cata-strophic failure of a bull gear compressor

Variations in demand or backpressure on a cantilever design can cause the entire rotating element and its shaft to flex This not only affects the compressor’s efficiency but also accelerates wear and may lead to premature shaft or rotor failure

All compressor types have moving parts, high noise levels, high pressures, and high-temperature cylinder and discharge-piping surfaces

POSITIVEDISPLACEMENT

Positive-displacement compressors can be divided into two major classifications, rotary and reciprocating

Rotary

The rotary compressor is adaptable to direct drive by the use of induction motors

or multi-cylinder gasoline or diesel engines These compressors are compact, relatively inexpensive, and require a minimum of operating attention and main-tenance They occupy a fraction of the space and weight of a reciprocating machine having equivalent capacity

Configuration

Rotary compressors are classified into three general groups: sliding vane, helical lobe, and liquid-seal ring

Sliding Vane The basic element of the sliding-vane compressor is the cylindrical housing and the rotor assembly This compressor, which is illustrated in Figure 12.5, has longitudinal vanes that slide radially in a slotted rotor mounted eccentrically in a cylinder The centrifugal force carries the sliding vanes against the cylindrical case with the vanes forming a number of individual longitudinal cells in the eccentric annulus between the case and rotor The suction port is located where the longitudinal cells are largest The size of each cell is reduced by

the eccentricity of the rotor as the vanes approach the discharge port, thus compressing the gas

Cyclical opening and closing of the inlet and discharge ports occurs by the rotor’s vanes passing over them The inlet port is normally a wide opening that

is designed to admit gas in the pocket between two vanes The port closes momentarily when the second vane of each air-containing pocket passes over the inlet port

When running at design pressure, the theoretical operation curves are identical (Figure 12.6) to a reciprocating compressor However, there is one major differ-ence between a sliding-vane and a reciprocating compressor The reciprocating unit has spring-loaded valves that open automatically with small pressure differ-entials between the outside and inside cylinder The sliding-vane compressor has

no valves

The fundamental design considerations of a sliding-vane compressor are the rotor assembly, cylinder housing, and the lubrication system

Housing and Rotor Assembly Cast iron is the standard material used to construct the cylindrical housing, but other materials may be used if corrosive conditions exist The rotor is usually a continuous piece of steel that includes the shaft and is made from bar stock Special materials can be selected for corrosive applications Occasionally, the rotor may be a separate iron casting keyed to a shaft On most standard air compressors, the rotor-shaft seals are semi-metallic packing in a stuffing box Commercial mechanical rotary seals can be supplied when needed Cylindrical roller bearings are generally used in these assemblies

Vanes are usually asbestos or cotton cloth impregnated with a phenolic resin Bronze or aluminum also may be used for vane construction Each vane fits into

Figure 12.5 Rotary sliding-vane compressor

a milled slot extending the full length of the rotor and slides radially in and out of this slot once per revolution Vanes are the most maintenance-prone part in the compressor There are from 8 to 20 vanes on each rotor, depending on its diameter A greater number of vanes increases compartmentalization, which reduces the pressure differential across each vane

Lubrication System A V-belt-driven, force-fed oil lubrication system is used on water-cooled compressors Oil goes to both bearings and to several points in the cylinder Ten times as much oil is recommended to lubricate the rotary cylinder

as is required for the cylinder of a corresponding reciprocating compressor The oil carried over with the gas to the line may be reduced 50% with an oil separator

on the discharge Use of an aftercooler ahead of the separator permits removal of 85-90% of the entrained oil

Helical Lobe or Screw The helical lobe, or screw, compressor is shown in Figure 12.7 It has two or more mating sets of lobe-type rotors mounted in a common housing The male lobe, or rotor, is usually direct-driven by an electric motor The female lobe, or mating rotor, is driven by a helical gear set that is mounted

on the outboard end of the rotor shafts The gears provide both motive power for the female rotor and absolute timing between the rotors

VOLUME

VOLUME VOLUME

DESIGN PRESSURE (DISCHARGE)

DESIGN PRESSURE DISCHARGE PRESSURE

OPERATION AT DESIGN PRESSURE

OPERATION ABOVE DESIGN PRESSURE

OPERATION BELOW DESIGN PRESSURE

DESIGN PRESSURE DISCHARGE PRESSURE

Figure 12.6 Theoretical operation curves for rotary compressors with built-in porting

The rotor set has extremely close mating clearance (i.e., about 0.5 mil) but no metal-to-metal contact Most of these compressors are designed for oil-free oper-ation In other words, no oil is used to lubricate or seal the rotors Instead, oil lubrication is limited to the timing gears and bearings that are outside the air chamber Because of this, maintaining proper clearance between the two rotors is critical

This type of compressor is classified as a constant volume, variable-pressure machine that is quite similar to the vane-type rotary in general characteristics Both have a built-in compression ratio

Helical-lobe compressors are best suited for base-load applications where they can provide a constant volume and pressure of discharge gas The only recommended method of volume control is the use of variable-speed motors With variable-speed drives, capacity variations can be obtained with a proportionate reduction in speed A 50% speed reduction is the maximum permissible control range Helical-lobe compressors are not designed for frequent or constant cycles be-tween load and no-load operation Each time the compressor unloads, the rotors tend to thrust axially Even though the rotors have a substantial thrust bearing and, in some cases, a balancing piston to counteract axial thrust, the axial clearance increases each time the compressor unloads Over time, this clearance will increase enough to permit a dramatic rise in the impact energy created by axial thrust during the transient from loaded to unloaded conditions In extreme cases, the energy can be enough to physically push the rotor assembly through the compressor housing

Figure 12.7 Helical lobe, or screw, rotary air compressor

Compression ratio and maximum inlet temperature determine the maximum discharge temperature of these compressors Discharge temperatures must be limited to prevent excessive distortion between the inlet and discharge ends of the casing and rotor expansion High-pressure units are water-jacketed to obtain uniform casing temperature Rotors also may be cooled to permit a higher operating temperature

If either casing distortion or rotor expansion occur, the clearance between the rotating parts will decrease and metal-to-metal contact will occur Since the rotors typically rotate at speeds between 3,600 and 10,000 rpm, metal-to-metal contact normally results in instantaneous, catastrophic compressor failure Changes in differential pressures can be caused by variations in either inlet or discharge conditions (i.e., temperature, volume, or pressure) Such changes can cause the rotors to become unstable and change the load zones in the shaft-support bearings The result is premature wear and/or failure of the bearings Always install a relief valve that is capable of bypassing the full-load capacity of the compressor between its discharge port and the first isolation valve Since helical-lobe compressors are less tolerant to over-pressure operation, safety valves are usually set within 10% of absolute discharge pressure, or 5 psi, whichever is lower

Liquid-Seal Ring The liquid-ring, or liquid-piston, compressor is shown in Figure 12.8 It has a rotor with multiple forward-turned blades that rotate about a central cone that contains inlet and discharge ports Liquid is trapped

Figure 12.8 Liquid-seal ring rotary air compressor

between adjacent blades, which drive the liquid around the inside of an elliptical casing As the rotor turns, the liquid face moves in and out of this space because

of the casing shape, creating a liquid piston Porting in the central cone is built-in and fixed and there are no valves

Compression occurs within the pockets or chambers between the blades before the discharge port is uncovered Since the port location must be designed and built for a specific compression ratio, it tends to operate above or below the design pressure (refer back to Figure 12.6)

Liquid-ring compressors are cooled directly rather than by jacketed casing walls The cooling liquid is fed into the casing, where it comes into direct contact with the gas being compressed The excess liquid is discharged with the gas The discharged mixture is passed through a conventional baffle or centrifugal-type separator to remove the free liquid Because of the intimate contact of gas and liquid, the final discharge temperature can be held close to the inlet cooling water temperature However, the discharge gas is saturated with liquid at the discharge temperature of the liquid

The amount of liquid passed through the compressor is not critical and can be varied to obtain the desired results The unit will not be damaged if a large quantity of liquid inadvertently enters its suction port

Lubrication is required only in the bearings, which are generally located external

to the casing The liquid itself acts as a lubricant, sealing medium, and coolant for the stuffing boxes

Performance

Performance of a rotary positive-displacement compressor can be evaluated by using the same criteria as used with a positive-displacement pump Because these are constant-volume machines, performance is determined by rotation speed, internal slip, and total backpressure on the compressor

The volumetric output of rotary positive-displacement compressors can be con-trolled by speed changes The slower the compressor turns, the lower its output volume This feature permits the use of these compressors in load-following applications However, care must be taken to prevent sudden radical changes in speed

Internal slip is simply the amount of gas that can flow through internal clear-ances from the discharge back to the inlet Obviously, internal wear will increase internal slip